A six-leaf rotary high-pressure cleaning spray head

Abstract

The application provides a six-leaf rotary high-pressure cleaning nozzle, and belongs to the technical field of high-pressure cleaning equipment. The six-leaf rotary high-pressure cleaning nozzle comprises a liquid connector, a pressure stabilizing cavity, an end cover, a six-leaf turbine component, a spray hole composite module, a variable speed connecting assembly, a nozzle, a shroud assembly and a damping and silencing mechanism. High-pressure fluid can drive the turbine at the inlet end of the pressure stabilizing cavity to rotate at high speed. The power is transmitted through the meshing of the first bevel gear and the second bevel gear to realize speed reduction and torque increase, drive the flow distribution seat and the nozzle to rotate stably and clean. The turbine adopts a six-leaf structure to improve the energy conversion efficiency and the rotation stability, and the conical structure of the cone seat guides the flow to eliminate the liquid flow impact. The thrust bearing bears the axial thrust to ensure stable operation. In addition, the device is also provided with a damping and silencing mechanism, a first vortex breaking surface and a second vortex breaking surface, which can effectively absorb vibration, reduce noise and optimize the flow state. The six-leaf rotary high-pressure cleaning nozzle has the advantages of stable operation, high cleaning efficiency and long service life.

Description

Technical Field

[0001] This invention relates to the field of high-pressure cleaning equipment technology, and in particular to a six-bladed rotating high-pressure cleaning nozzle. Background Technology

[0002] High-pressure water jet cleaning technology, as a highly efficient and environmentally friendly physical cleaning method, is widely used in industrial cleaning and pipeline dredging. In cleaning operations, rotating nozzles have become a key component to maximize the coverage area and improve cleaning efficiency per operation. Traditional rotating nozzles typically utilize water flow to drive an internal impeller or turbine to rotate at high speed, thereby causing the nozzle to perform circumferential scanning spraying.

[0003] However, existing water-driven rotary nozzles still have the following significant technical drawbacks in practical applications: First, existing water turbines directly drive the nozzle rotation. To obtain sufficient cleaning impact force, extremely high water flow velocities are often required, leading to excessively high nozzle rotation speeds. Excessive speed not only results in a short residence time of the water jet on the cleaning surface, affecting the removal of dirt, but also easily causes equipment vibration due to excessive centrifugal force. Second, the internal flow field of the nozzle is turbulent, resulting in significant energy loss. After the high-pressure water flow enters the nozzle and drives the turbine to rotate at high speed, eddies and turbulence are easily generated. Existing nozzle structures often lack effective rectification and eddy-breaking designs, leading to ineffective energy consumption of the fluid internally. This not only reduces the effective pressure driving the turbine but also exacerbates vibration and noise within the nozzle. In addition, traditional nozzles often use three- or four-bladed turbines. The small number of blades leads to uneven distribution of fluid forces, which can easily cause rotational vibration and pressure pulsation, resulting in low energy conversion efficiency. On the other hand, too many blades can block the flow channel, increase flow resistance, and make the turbine start-up sensitivity low and the operation smooth, making it difficult to provide continuous and stable power support, thus affecting the uniformity of the cleaning operation. Summary of the Invention

[0004] The purpose of this invention is to provide a six-blade rotating high-pressure cleaning nozzle, which aims to solve problems such as excessive nozzle rotation speed and turbulent flow field in the prior art.

[0005] The objective of this invention is achieved through the following technical solution: a six-blade rotary high-pressure cleaning nozzle, comprising a pressure stabilizing chamber, a six-blade turbine component, a nozzle composite module, and a speed-changing connection assembly. The pressure stabilizing chamber includes a pressure stabilizing chamber body and a liquid outlet chamber. The six-blade turbine component includes a turbine. The nozzle composite module includes a flow divider. The speed-changing connection assembly includes a first bevel gear. The liquid outlet chamber is connected to the pressure stabilizing chamber, and the two form an angle of less than 90 degrees between their axes. The inner cavity at the connection between the pressure stabilizing chamber and the liquid outlet chamber is provided with a first vortex-breaking surface and a second vortex-breaking surface on both sides. The first vortex-breaking surface and the second vortex-breaking surface form a variable diameter constriction structure in the inner cavity at the connection between the pressure stabilizing chamber and the liquid outlet chamber. A turbine shaft is rotatably connected to the inner center of the pressure stabilizing chamber. The turbine is located at the inlet of the pressure stabilizing chamber and is fixedly connected to one end of the turbine shaft. The first bevel gear is fixed to the other end of the turbine shaft. A rotating cylinder shaft is rotatably connected to the inner center of the liquid outlet chamber. A flow divider is located at the outlet of the liquid outlet chamber, and the middle of the flow divider is fixedly connected to one end of the rotating cylinder shaft. A second bevel gear is fixedly connected to the other end of the rotating cylinder shaft. The second bevel gear meshes with the first bevel gear. Flow channels are evenly opened in the main body of the turbine. Nozzles are evenly connected to the side wall of the flow divider.

[0006] The technical solution of this invention is used as follows: The high-pressure cleaning fluid first enters the inlet of the pressure stabilizing chamber, directly impacting the turbine blades located there, and then passes through the flow channels evenly distributed in the turbine body; the fluid's kinetic and pressure energy are converted into mechanical energy, driving the turbine to rotate at high speed around the turbine shaft. The fluid driving the turbine to rotate continues to flow forward and enters the main body of the pressure stabilizing chamber. At this time, the first and second vortex-breaking surfaces connected to the inner sides of the pressure stabilizing chamber and the liquid outlet chamber play a role. The first and second vortex-breaking surfaces form a variable diameter constriction structure at the connection between the pressure stabilizing chamber and the liquid outlet chamber, which can rectify the fluid, eliminate vortices and turbulence caused by the turbine changing the flow direction, ensure that the fluid pressure entering the liquid outlet chamber is stable and the flow is smooth, and reduce energy loss. The high-speed rotation of the turbine shaft drives the first bevel gear to rotate, and the first bevel gear meshes with the second bevel gear fixed to the end of the drum shaft. According to the principle of gear transmission, when the small gear drives the large gear to rotate, the speed reduction operation is achieved. This design converts the high speed of the turbine into the low speed output of the drum shaft. In addition, the meshing of the second bevel gear with the first bevel gear also changes the direction of power transmission, enabling the drum shaft to operate smoothly in the liquid outlet chamber. The low-speed rotation of the rotating drum shaft drives the flow divider fixed to it to rotate synchronously; the high-pressure fluid enters the flow divider through the liquid outlet chamber and is finally powerfully ejected from the nozzles that are uniformly connected to the side wall of the flow divider. Because the distributor seat is in a stable rotating state, the high-pressure water jet ejected from the nozzle forms a rotating cleaning trajectory (such as a circular or spiral scan), which significantly expands the coverage area of ​​a single cleaning compared to a fixed nozzle, improving cleaning efficiency and uniformity.

[0007] By adopting the above technical solution, the present invention can achieve the following beneficial effects: (1) The present invention sets the turbine as a six-blade structure, which has significant advantages in fluid dynamics. The six blades are evenly distributed, which can make the high-pressure water flow entering the pressure stabilizing cavity impact the blade surface more evenly, avoiding uneven force and rotational vibration caused by too few blades. At the same time, it avoids the flow channel blockage and energy loss caused by too many blades. The six-blade structure can maximize the capture of the kinetic and pressure energy of the water flow while ensuring sufficient flow area, converting more fluid energy into mechanical energy, making the turbine start more sensitive and the rotation more stable, providing continuous and stable power support for the subsequent deceleration transmission and the nozzle rotation with the flow divider. (2) Furthermore, the six-bladed structure of the turbine, due to its balanced force and smooth operation, allows the fluid to form a more regular flow trajectory after passing through the flow channel in the turbine. Compared with the irregular vortex caused by uneven force when there are too few blades, or the violent turbulence caused by flow channel blockage when there are too many blades, the six-bladed turbine can make the fluid flow state more orderly, which provides a good precondition for the subsequent rectification of the first and second vortex breaking surfaces. The variable diameter constriction structure formed by the first and second vortex breaking surfaces at the connection between the pressure stabilizing cavity and the liquid outlet cavity can rectify the fluid passing through the turbine, so that the rectified fluid enters the liquid outlet cavity with a smoother flow state, avoiding pressure fluctuations and energy dissipation caused by vortices and turbulence, and enabling the mechanical energy converted by the six-bladed turbine to be transferred to the subsequent speed-changing connection components and nozzle composite modules more efficiently. (3) The present invention cleverly constructs a speed reduction transmission mechanism through the meshing of the first bevel gear and the second bevel gear; this design converts the high speed generated by the turbine impacted by the water flow into the low speed and high torque output of the rotating drum shaft, which increases the output torque while reducing the speed, effectively solving the problems of rotation jamming and stopping caused by insufficient torque in traditional water-driven nozzles, ensuring that the nozzle can maintain a stable rotation state under high pressure water flow. Combined with the vortex breaking and rectification effect of the first and second vortex breaking surfaces, the fluid energy loss is further reduced, making the power transmission smoother and significantly improving the continuity and reliability of the cleaning operation. Attached Figure Description

[0008] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0009] Figure 1 This is a schematic diagram of the overall exploded structure of the present invention; Figure 2 This is an overall schematic diagram of the present invention; Figure 3This is a cross-sectional schematic diagram of the present invention; Figure 4 This is a schematic diagram of the internal transmission structure of the present invention; Figure 5 This is a schematic diagram of the cone-shaped support portion of the present invention; Figure 6 This is a schematic diagram of the structure of the protective cover assembly of the present invention; Figure 7 This is a cross-sectional schematic diagram of the nozzle portion of the present invention.

[0010] Figure label: 1. Liquid inlet connector; 2. Pressure stabilizing chamber; 3. End cap; 4. Six-bladed turbine component; 5. Nozzle composite module; 6. Speed ​​change connection assembly; 7. Nozzle; 8. Protective cover assembly; 9. Vibration damping and noise reduction mechanism; 10. O-ring; 201. Pressure stabilizing chamber; 202. Liquid outlet chamber; 203. First vortex-breaking surface; 204. Second vortex-breaking surface; 401. Turbine; 402. Flow passage; 403. Turbine sleeve; 404. Turbine shaft seat; 405. Turbine shaft seal 406. Turbine shaft; 501. Rotary cylinder sealing sleeve; 502. Rotary cylinder; 503. Flow divider seat; 504. Rotary cylinder shaft; 505. Rotary cylinder shaft seat; 506. Rotary cylinder shaft sealing sleeve; 507. Cone seat; 508. Thrust bearing; 601. First bevel gear; 602. Second bevel gear; 801. Fixed seat; 802. Protective cover; 803. Connecting seat; 804. Irregular sealing gasket; 901. Vibration damping and noise reduction groove; 902. Vibration damping and noise reduction block. Detailed Implementation

[0011] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0012] In the description of this invention, it should be noted that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the invention and for simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0013] Example 1: like Figure 1-7 As shown, a six-bladed rotary high-pressure cleaning nozzle has a liquid outlet chamber 202 in the pressure stabilizing chamber 2 connected to the pressure stabilizing chamber 201, and the two form an angle of less than 90 degrees between their axes. The inner cavity at the connection between the pressure stabilizing chamber 201 and the liquid outlet chamber 202 is provided with a first vortex-breaking surface 203 and a second vortex-breaking surface 204 on both sides. The first vortex-breaking surface 203 and the second vortex-breaking surface 204 form a variable diameter constriction structure in the inner cavity at the connection between the pressure stabilizing chamber 201 and the liquid outlet chamber 202. A turbine shaft 406 is rotatably connected to the inner center of the pressure stabilizing chamber 201. The turbine 401 is located at the inlet of the pressure stabilizing chamber 201 and is fixedly connected to one end of the turbine shaft 406. A first bevel gear 601 is fixed to the other end of the turbine shaft 406 and is located outside the pressure stabilizing chamber 201. A rotating drum shaft 504 is rotatably connected to the inner center of the liquid outlet chamber 202. A flow divider 503 is located at the outlet of the liquid outlet chamber 202. The middle part is fixedly connected to one end of the rotating drum shaft 504, and the other end of the rotating drum shaft 504 is fixedly connected to the second bevel gear 602. The second bevel gear 602 meshes with the first bevel gear 601. The turbine 401 body is evenly provided with flow passages 402. The side wall of the flow divider 503 is evenly connected with nozzles 7. The connection position between the nozzles 7 and the flow divider 503 is provided with O-rings 10. The nozzles 7 are threadedly connected to the cavity wall of the flow divider 503. The O-rings 10 are installed at the threaded connection position. The working principle is as follows: The high-pressure cleaning fluid first enters the inlet of the pressure stabilizing chamber 201, directly impacting the blades of the turbine 401 located there, and passes through the flow channels 402 evenly opened in the turbine 401 body; the kinetic and pressure energy of the fluid is converted into mechanical energy, driving the turbine 401 to generate high-speed rotation around the turbine shaft 406. The fluid driving the turbine 401 to rotate continues to flow forward and enters the main body of the pressure stabilizing chamber 201. At this time, the first vortex-breaking surface 203 and the second vortex-breaking surface 204 connected on both sides of the inner cavity of the pressure stabilizing chamber 201 and the liquid outlet chamber 202 play a role. The first vortex-breaking surface 203 and the second vortex-breaking surface 204 form a variable diameter constriction structure at the connection between the pressure stabilizing chamber 201 and the liquid outlet chamber 202, which can rectify the fluid, eliminate vortices and turbulence caused by the turbine 401 changing the flow direction, ensure that the fluid pressure entering the liquid outlet chamber 202 is stable and the flow is smooth, and reduce energy loss. The high-speed rotation of the turbine shaft 406 drives the first bevel gear 601 to rotate accordingly. The first bevel gear 601 meshes with the second bevel gear 602 fixed to the end of the rotating drum shaft 504. According to the gear transmission principle, when the small gear drives the large gear to rotate, the speed reduction operation is realized. This design converts the high speed of the turbine 401 into the low speed output of the rotating drum shaft 504. In addition, the meshing of the second bevel gear 602 with the first bevel gear 601 also changes the direction of power transmission, enabling the rotating drum shaft 504 to operate smoothly in the liquid outlet chamber 202. The low-speed rotation of the rotating drum shaft 504 drives the flow divider 503 fixed to it to rotate synchronously; the high-pressure fluid enters the flow divider 503 through the liquid outlet chamber 202, and is finally powerfully ejected from the nozzles 7 uniformly connected to the side wall of the flow divider 503. Since the diverter seat 503 is in a stable rotating state, the high-pressure water jet ejected by the nozzle 7 forms a rotating cleaning trajectory (such as a circular or spiral scan), which significantly expands the single cleaning coverage area and improves cleaning efficiency and uniformity compared to a fixed nozzle. The pressure stabilizing chamber 201 is connected to a liquid inlet connector 1 at the inlet position, and the inlet end of the liquid inlet connector 1 is quickly connected to an external high-pressure liquid pipeline. Specifically, the inlet of liquid inlet connector 1 adopts a quick-connect structure, which can quickly connect with external high-pressure liquid pipelines, making it easy to operate and providing good sealing.

[0014] The specific structure of the six-bladed turbine component 4 and the nozzle composite module 5 is as follows: Figure 1 , Figure 2 , Figure 3 , Figure 4 and Figure 5 As shown, a turbine sleeve 403 is installed at the inlet end of the pressure stabilizing chamber 201. The outer cylindrical surface of the turbine 401 is rotatably connected to the turbine sleeve 403, which can effectively prevent the turbine 401 from axially moving or radially shifting under the impact of high-pressure water flow. A turbine shaft seat 404 is fixedly connected to the main body of the first vortex breaking surface 203. A turbine shaft sealing sleeve 405 is installed and fixed on the inner end of the turbine shaft seat 404. The turbine shaft 406 is rotatably connected to the turbine shaft sealing sleeve 405, and the turbine shaft sealing sleeve 405 is used to block the high-pressure cleaning fluid from leaking along the turbine shaft 406 axially. The turbine shaft sealing sleeve 405 adopts a mature end-face mechanical seal structure (such as a sealed bearing) in existing technology. It has a dynamic ring and a stationary ring inside. The turbine shaft 406 passes through the turbine shaft sealing sleeve 405 and is fixedly connected to its dynamic ring, while the stationary ring is fixed inside the turbine shaft seat 404. When the turbine shaft 406 rotates at high speed, the end faces of the dynamic ring and the stationary ring are tightly fitted under the action of spring force and fluid pressure, forming a stable end-face sealing structure. This structure not only provides reliable radial and axial rotation support points for the turbine shaft 406, but also uses wear-resistant materials such as precision-machined hard alloy or silicon carbide as sealing surfaces, which can effectively prevent high-pressure cleaning fluid from leaking along the axis of the turbine shaft 406 to the transmission area of ​​the first bevel gear 601. This design ensures that the turbine shaft 406 can rotate smoothly in it, and avoids power loss and corrosion of transmission components caused by fluid leakage, which greatly improves the sealing performance and service life of the entire device. An end cap 3 is fixedly connected to the outlet end of the liquid outlet chamber 202. A rotating cylinder sealing sleeve 501 is installed and fixed inside the end cap 3. The rotating cylinder 502 is rotatably connected in the rotating cylinder sealing sleeve 501. The flow divider 503 is fixedly connected to the rotating cylinder 502, and the inner cavities of the rotating cylinder 502 and the flow divider 503 are connected. The main body of the first vortex breaking surface 203 is also fixedly connected to a rotating drum shaft seat 505, and a rotating drum shaft sealing sleeve 506 is installed and fixed on the inner end of the rotating drum shaft seat 505. The rotating drum shaft 504 is rotatably connected to the rotating drum shaft sealing sleeve 506. Similarly, the structures of the rotary drum sealing sleeve 501 and the rotary drum shaft sealing sleeve 506 are the same as those of the turbine shaft sealing sleeve 405, only the specifications and models are different. They are all used to prevent leakage of high-pressure cleaning fluid while ensuring rotation. A conical seat 507 is also fitted in the main body of the turbine shaft 406 and the drum shaft 504. A thrust bearing 508 is installed and fixed at the large conical end of the conical seat 507. The thrust bearing 508 is connected between the inner end of the turbine shaft seat 404 and the conical seat 507, or between the inner end of the drum shaft seat 505 and the conical seat 507. By fixing the cone seat 507 in both the turbine shaft 406 and the drum shaft 504, the cone structure of the cone seat 507 can be used to guide the fluid movement and eliminate the direct impact of high-speed liquid flow on the turbine shaft seat 404 or the drum shaft seat 505. The thrust bearing 508 can limit the axial displacement of the turbine shaft 406 and the drum shaft 504, ensuring the smooth rotation of the turbine shaft 406 and the drum shaft 504 and reducing mechanical wear.

[0015] Example 2: The specific structure of the protective cover assembly 8 installed on the outer side of the connection between the pressure stabilizing chamber 201 and the liquid outlet chamber 202 is as follows: Figure 6As shown, a base 801 is evenly fixed on the outer side of the connection between the pressure stabilizing chamber 201 and the liquid outlet chamber 202. The protective cover 802, carrying a special-shaped sealing gasket 804, is fastened to the outer side of the connection between the pressure stabilizing chamber 201 and the liquid outlet chamber 202. A connecting seat 803 is evenly arranged in the main body of the protective cover 802. The connecting seat 803 on the same side is fastened to the base 801. A standard screw can be screwed into the base 801 through the connecting seat 803 to achieve the fixation of the protective cover 802 and the base 801. Before installing the protective cover 802, lubricating grease should be applied fully to the meshing position of the first bevel gear 601 and the second bevel gear 602 to reduce friction, reduce wear, and extend the service life of the gears.

[0016] Example 3: The specific structure of the vibration damping and noise reduction mechanism 9 installed in the main body of the second vortex surface 204 is as follows: Figure 2 , Figure 3 and Figure 4 As shown, the vibration damping and noise reduction slot 901 is opened on the outer side of the main body of the second vortex breaking surface 204 and is not connected to the inner cavity of the pressure stabilizing cavity 201 and the liquid outlet cavity 202. The vibration damping and noise reduction block 902 is fixed in the vibration damping and noise reduction slot 901. The vibration damping and noise reduction block 902 is made of high-damping rubber material (such as natural rubber, nitrile rubber or fluororubber, etc.), which has excellent elasticity, high damping characteristics and good fatigue resistance. When the high-pressure cleaning nozzle is running at high speed in the internal turbine 401 and the fluid is moving violently, the high-pressure liquid will generate high-frequency pulsating impact when it flows through the second vortex surface 204. The damping and noise reduction block 902 can play a flexible buffering role, weaken the rigid impact of the fluid, and reduce the structural resonance caused by fluid excitation.

[0017] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A six-blade rotary high-pressure cleaning nozzle, comprising a pressure stabilizing chamber (2), characterized in that: It also includes a six-bladed turbine component (4), a nozzle composite module (5), and a speed change connection assembly (6); The pressure stabilizing chamber (2) includes a pressure stabilizing chamber body (201) and a liquid outlet chamber body (202); the six-bladed turbine component (4) includes a turbine (401); the nozzle composite module (5) includes a flow divider (503); and the speed change connection assembly (6) includes a first bevel gear (601). The liquid outlet chamber (202) is connected to the pressure stabilizing chamber (201), and the two form an angle of less than 90 degrees between their axes. The inner cavity at the connection between the pressure stabilizing chamber (201) and the liquid outlet chamber (202) is provided with a first vortex-breaking surface (203) and a second vortex-breaking surface (204) on both sides respectively. The first vortex-breaking surface (203) and the second vortex-breaking surface (204) form a variable diameter constriction structure in the inner cavity at the connection between the pressure stabilizing chamber (201) and the liquid outlet chamber (202). A turbine shaft (406) is rotatably connected to the inner center of the pressure stabilizing chamber (201). The turbine (401) is located at the inlet of the pressure stabilizing chamber (201) and is fixed to one end of the turbine shaft (406). The first bevel gear (601) is fixed to the other end of the turbine shaft (406). A rotating drum shaft (504) is rotatably connected to the inner center of the liquid outlet chamber (202). A flow divider (503) is located at the outlet of the liquid outlet chamber (202). The middle part of the flow divider (503) is fixed to one end of the rotating drum shaft (504). The other end of the rotating drum shaft (504) is fixed to a second bevel gear (602). The second bevel gear (602) meshes with the first bevel gear (601). Flow channels (402) are evenly opened in the body of the turbine (401). Nozzles (7) are evenly connected to the side wall of the flow divider (503).

2. The six-blade rotary high-pressure cleaning nozzle according to claim 1, characterized in that: The pressure stabilizing chamber (201) is connected to a liquid inlet connector (1), and the inlet end of the liquid inlet connector (1) is quickly connected to an external high-pressure liquid pipeline.

3. A six-blade rotary high-pressure cleaning nozzle according to claim 2, characterized in that: The six-bladed turbine component (4) also includes a turbine shaft sealing sleeve (405), a turbine sleeve (403) is installed at the inlet end of the pressure stabilizing cavity (201), the outer cylindrical surface of the turbine (401) is rotatably connected to the turbine sleeve (403), and the main body of the turbine (401) is located in the inner cavity of the liquid inlet connector (1). A turbine shaft seat (404) is fixed in the main body of the first vortex breaking surface (203), the turbine shaft sealing sleeve (405) is installed and fixed in the inner end of the turbine shaft seat (404), and the turbine shaft (406) is rotatably connected to the turbine shaft sealing sleeve (405).

4. A six-blade rotary high-pressure cleaning nozzle according to claim 1, 2, or 3, characterized in that: The nozzle composite module (5) also includes a rotating drum (502) and a rotating drum shaft sealing sleeve (506). An end cap (3) is fixedly connected to the outlet end of the liquid outlet chamber (202). A rotating drum sealing sleeve (501) is installed and fixed inside the end cap (3). The rotating drum (502) is rotatably connected in the rotating drum sealing sleeve (501). The flow divider (503) is fixedly connected to the rotating drum (502). A rotating drum shaft seat (505) is also fixedly connected in the main body of the first vortex breaking surface (203). The rotating drum shaft sealing sleeve (506) is installed and fixed in the inner end of the rotating drum shaft seat (505). The rotating drum shaft (504) is rotatably connected to the rotating drum shaft sealing sleeve (506).

5. A six-blade rotary high-pressure cleaning nozzle according to claim 4, characterized in that: The turbine shaft (406) and the main body of the drum shaft (504) are also fitted with a conical seat (507). A thrust bearing (508) is installed and fixed at the large conical end of the conical seat (507). The thrust bearing (508) is connected between the inner end of the turbine shaft seat (404) and the conical seat (507), or between the inner end of the drum shaft seat (505) and the conical seat (507).

6. A six-blade rotary high-pressure cleaning nozzle according to claim 1, 2, 3, or 5, characterized in that: A protective cover assembly (8) is installed on the outer side of the connection between the pressure stabilizing chamber (201) and the liquid outlet chamber (202). The protective cover assembly (8) includes a protective cover (802) and a shaped sealing gasket (804). A fixed seat (801) is uniformly fixed on the outer side of the connection between the pressure stabilizing chamber (201) and the liquid outlet chamber (202). The protective cover (802) carrying the shaped sealing gasket (804) is fastened to the outer side of the connection between the pressure stabilizing chamber (201) and the liquid outlet chamber (202). A connecting seat (803) is uniformly arranged in the main body of the protective cover (802). The connecting seat (803) on the same side is fastened to the fixed seat (801).

7. A six-blade rotary high-pressure cleaning nozzle according to claim 1, 2, 3, or 5, characterized in that: The main body of the second vortex surface (204) is also equipped with a vibration damping and noise reduction mechanism (9). The vibration damping and noise reduction mechanism (9) includes a vibration damping and noise reduction slot (901) and a vibration damping and noise reduction block (902). The vibration damping and noise reduction slot (901) is opened on the outside of the main body of the second vortex surface (204), and the vibration damping and noise reduction block (902) is fixed in the vibration damping and noise reduction slot (901).

8. A six-blade rotary high-pressure cleaning nozzle according to claim 1, 2, 3, or 5, characterized in that: An O-ring (10) is provided at the connection position between the nozzle (7) and the flow divider (503). The nozzle (7) is threadedly connected to the cavity wall of the flow divider (503), and the O-ring (10) is installed at this threaded connection position.

Images